Speed change power transmission



y 1936- J. MISIAK, JR

SPEED CHANGE POWER TRANSMISSION Filed Dec. 29, 19335 3 Sheets-Sheet 1 May 26, 1936.

J. MISIAK. JR

SPEED CHANGE POWER TRANSMISSION File d Dec. 29, 1953 3 Sheets-Sheet; 2

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SPEED CHANGE POWER TRANS MI SION Filed Dec. 29, 1953 3 Sheets-Sheet s 1311061110)? 115711711 JWZJSL GJU f ulA/XM Patented May 26, 1936 UNITED STATES PATENT OFFICE third to Lloyd Z.

Peck, Chicago, Ill.

Application December 29, 1933, Serial No. 704,397

21 Claims.

The present invention relates to improvements in power transmissions, and has for its primary object the provision of a new and improved-speed- *ichange power transmission in which the speed adjustments are automatically effected by progressive changes in member. v h Another object resides in the provision of a 'novel power transmission of the foregoing char: 1 acter which comprises an automatic slow speed clutch, and a plurality of automatic overload clutches for controlling the higher speed adjustments. v

A furtherobject is to provide a new and improved automaticspeed-change power transmission which comprises two parallel driving and driven shaft elements adapted to be connected selectively through any one of a plurality of parallel gear trains of different gear ratios.

Still another object resides in making each shaft' element in a plurality of axially aligned shaft sections which are connected for a unitary drive, and which are in telescoping and interfitting engagement,- thereby retaining them in a sturdy and compact assembled relation, preventing'lateral flexure and misalignment-and permitting ready assembly and disassembly.

A further object resides in the provision of novel means for providing an automatic reverse drive connection between the driven and driving shaft elements when the power to the latter is discontinued.

Another object resides in the provision of a acting clutch elements are urged toward each other by yieldable means, and are urged apart by the torque of the drive against the action of the yieldable means, the torque when exceeding apredetermined-value, determined by the pressure of the yieldablemeans,-acting automatically to'efiecta complete separation of the elefullyself-adjusting. Further objects and advantages will become fapparentflasj the description proceeds; I v

In the accompanying drawings, Figure 1 is a sideelevational view, with the casing in section,

. of a transmission embodying the features of 'my the torque set up by the driven novel automatic overload clutch in which the cotransmission adjusted for an intermediate speed drive.

Fig. 3 is a transverse sectional view of one of the automatic overload clutches taken along line 3- 3 of Fig. 2.

Fig. 4 is a transverse sectional view of one of the shaft couplings taken along line 4-4 of Fig. 2. I Fig. 5 is a perspective view of one of the automatic overload clutches and the associated shaft coupling in disassembled relation.

Fig. 6 is a transverse sectional view of one of the overrunning clutches in the driven shaft assembly and the associated coupling taken along line 6-6 of Fig. 2.

Fig. 7 is a perspective view of the construc- 10 tion illustrated in Fig. 6 with the parts in disassembled relation.

Fig. 8 is a sectional detail view taken along line 88 of Fig. 2.

While the invention is susceptible of various modifications and alternative constructions, I have shown in the drawings and will herein describe in detail the preferred embodiment, but it is to be understood that I do not thereby intend to limit the invention to the specific form disclosed, but intend to cover all modifications and alternative constructions falling within the spirit and scope of the invention as expressed in the appended claims.

Referring more particularly tothe drawings, the power transmission in its preferred form comprises an external housing 8, a driving or power inlet shaft element 9 adapted to be connected to a suitable source of power (not shown), and a driven or power outlet shaft element ID. A plurality of drive connections of different speed ratios are selectively available through the operation of a plurality of automatic clutches to connect the shaft elements 9 and Ill. The clutches are torque controlled, and, as the load on the driven ,shaft element III is gradually decreased, serve to close the drive connections successively to progressively increase the speed ratio between the shaft elements 9 and I0.

While the transmission may be used for various purposes, it is particularly adapted for use in the forward drive of motor vehicles, and hence is shown as comprising three parallel drive connections respectively including three automatic clutches II, II and I3, defining the usual high,

intermediate and low speed positions. The clutches operate automatically and in sequence, and obviate the hand shifting of gears ordinarily employed. r

The driving shaft element or assembly 9 con- I83 in the' periphery of the member I88 serve to lock the members against relative rotation in one direction. One end of the shaft 99 extends externally of the housing 8 through a packing box I9 for connection to the source of power, and

the other end thereof is formed with an axial bore I84. The packing box i9 overlies the outside of the bearing [1, and hence seals the housing 8 at this point against the entry of foreign matter and the loss of lubricant. The shaft 14 is formed in its inner end with an axial bore 28 and on its outer end with an axial extension I85 projecting into the bore I84. The second or intermediate shaft section I5 is tubular in form, and abuts at one end against the inner end of the section l4. The third shaft section I8 is journaled at one end in a ball bearing 2| mounted in the adjacent end, wall 22 of the housing 8, and closed externally by a cover plate 23. At its other end, the shaft section I8 has a reduced axial extension 24 which defines an annular shoulder 25 at its base, and which projects: through the intermediate shaft section l5 into the bore 28 to hold all of the sections in assembled relation. Thus, the intermediate shaft section 15 is rotatably confined on the shaft extension 24 between the inner end of the first shaft section l4 and the shoulder 25.

The shaft sections l4, l5 and I8 of the driving shaft assembly are connected for joint rotation. In'the present instance, the inner end of the inlet shaft section I4 is formed externally with a plurality of peripherally spaced and generally longitudinal spline keys 28 which slidably interfit with similar keys 21 formed in the interior of a sleeve member 28. The latter is formed with a coaxial sleeve 29 of somewhat larger diameter having internal peripherally spaced keys: 38 which slidably interflt with similarly spaced keys 3| on the periphery of a disk 32. The keys 38 and 3| are parallel to the axis of rotation. To secure the disk 32 for rotation with the intermediate shaft section 15, the end of the latter adjacent the section I4 is milled with diametrically opposed tangential notches 33, and the disk is formed with a similarly shaped opening '34 fitting into the notches. Thus, the inlet shaft section I4 is continuously connected through a spline coupling, consisting of the keys 28 and 21, the

sleeves 28 and 29, the keys 38 and 31 and the disk 32, to the intermediate shaft section a unitary drive. 9

A similar coupling is provided for connecting l5 for the intermediate shaft section 15 and the third faces of the notches 33 or 43 and the: adjacent end of the shaft section l4 or I 5. It will be evident that the driving shaft assembly 9 is held together solely by the interfitting and telescoping relationship of the parts, and that it may be readily assembled and disassembled upon removal of the packing i9 and the bearing I1.

The driven shaft element or assembly I8 is parallel to the driving shaft element 9-, and also comprises a plurality of axially aligned and end abutting shaft sections 44, 45, 48, 41 and 48. The first or outlet shaft section 44 is journaled in a ball bearing 49 mounted in a wall 58 within a sleeve 5| integral with the wall 22 and defining a housing 52 for a reversing mechanism (not shown). An annular cover plate 53 serves to close the exterior of the bearing 49. Of the shaft section 44, the outer end is adapted to be connected to the part to be driven, and the inner end is formed with an axial bore 54. The first intermediate shaft section 45 is relatively short, and is formed on one end with an axial extension 55 projecting rotatably in the bore 54 and in the other end with a bore 58. Likewise, the second intermediate shaft section 48 is formed in one end with an axial bore 51 and on the other end with an axial extension 58 projecting into the bore 58. The third intermediate shaft section 41- is short and tubular in form. The shaft section 48 is journaled at one end in a ball bearing 59 mounted in the wall l8 and closed externally by a cover plate 88, and at its other end is formed with a reduced axial extension 8| defining an annular shoulder 82 and extending through the intermediate section 41 into the bore 51. Thus, the intermediate shaft sections 45 to 41 arerotatably confined between the inner end of the outlet section 44 and the shoulder 82.

The sections 44, 45, 48, 41 and 48 are also interconnected by a series of couplings for a unitary rotation drive in one direction. Thus, the end of the shaft section 48 adjacent the shoulder 82 has generally longitudinal and uniformly peripherally spaced spline keys 83 slidably interfit sleeve 88. Both sets of keys 81 and 88 are parallel to the axis oi rotation. The sleeve 89 is formed milled diametrically opposed notches 12 -in the adjacent end of the intermediate shaft section 41.

Preferably, the couplings between the shaft sections 41 and 48, and 45 and 44 are similar, the first comprising keys- 13 and 14, sleeves 15 and .18, keys 11 and 18, a sleeve 19 and a disk 88 having an opening 8| interfitting with notches 82 in the section 48, and the second comprising .keys 83 and 84, sleeves 85 and 88, keys 81 and 88, a sleeve 89 and a disk 98 having an opening 9i interfltting with notches 92 in the inner'end of the outlet shaftsection 44.

In each instance, the disk (18, 88 or 98) is held removably in endwise position between the end faces of the associated notches (12, 82 or 92) and the adjacent end of the opposed shaft section (48, 41 or 45) As in the case of the driving shaft assembly 9, the parts of the driven shaft assembly 18 may be readily assembled and disassembled upon removal of the bearing 49 and the cover plate 53.

. The shaft sections 48 and 45 are connected by an overrunning clutch 93 which comprises concentric inner and outer coupling members 94 and 75 able on the intermediate shaft section I5 and 85 keyed respectively to the adjacent ends of the sections. The inner member 94 is formed in its periphery with wedge notches 96 in which wedge rollers 91 are disposed. The construction is similar to that shown in Fig. 8.

The high speed drive is-=taken from the inlet shaft section I4, and passes through the primary or high speed clutch II, a gear I06 freely rotatheld against endwise movement between the clutch I2 and the disk 32, and a gear I 01- integral with the shaft section 48 and meshing with the gear I06. The ratio between'the gears I06 and I01 is relatively low so that the clutch II is.

subjected to a relatively high torque through the driven shaft assembly l0.

- The clutch II may be of any suitable overload type. In its preferred form, the clutch II com prises two annularly arranged sets of opposed ratchet teeth I01 and I08 constituting clutch elements adapted for relative movement axially of the shaft section I4 into and out of coacting engagement.' Preferably, the teeth I01 and I08 have steep engaging faces with inclined backs.

The clutchteeth I01 areformed on one end face termediate shaft section I5 is maintained at all times. Preferably, an annular groove H is formed in one side of the gear I06 to receive the free end of the sleeve 29 when the clutch II is closed.

The clutch element I01 tends to move from the element I00 in response to the drivemesistance or rotational torque to which it is subjected.

Preferably, the keys 26 and ,21 constitute wedge means tending as an incident to the drive to open the clutch II, and to this end are slightly inclined or helical in one direction relative to the axis of rotation. The separating action is opposed by yieldable means tending to effect movement of the clutch element III1 toward the element I08. In the present instance, the yieldable means comprises a plurality of sets of compression leaf springs I II tending to rptate the clutch element I01 about the shaft section I4 in a direction to advance the element I01 along the keys 26. The springs III (see Fig. 3) are disposed in uniformly peripherally spaced relation about the sleeve member 28, and betweenthe clutch disk I06 and an opposed parallel backing disk or plate II2 integral and concentric with the inlet shaft section I4. An annular peripheral flange II3 on one side of the disk II2 serves to enclose the spring space. The springs III of each set are v U-shaped' in form and nested, with their ends extending outwardly and anchored respectively to two spaced pins H4 and H5 rigid with the disks I09 and H2. A plurality of lateral projections II6 extend from the disk I08 just inside the flange H3 and respectively over the pins II4.

tends to the inner surface of the associated projection I I6, and is confined between the pin H4 and the flange II1 for movement with the disk I 09.

In operation, the sleeve. member 28 is subjected to torque in overcoming the load on the driven shaft assembly I0. This torque, due to the wedge faces of the keys 26 and 21 imparts an axial thrust on the'clutch element I01 tending to open the clutch II against the resistance of the springs III. When the load is in excess of a predetermined value, for example, the maximum operate in high gear, the clutch II will be open.

adjustment. As the load decreases to-below this value, the'axial thrust imparted by the keys 26 and 21 decreases accordingly, and the springs I I I act to rotate the sleeve 20 relatively to the disk H2 in a clockwise direction as viewed in Fig. 3, thereby advancing the clutch element I01? by a screw action along the keys 26 into operative engagement with the clutch element I08. The springs III will suffer a slight lateral flexure to permit the attendant separation of the disks I09 and H2.

normal load under which a motor vehicle should p The intermediate speed drive is taken from the intermediate shaft section I5, and passes through the secondary or intermediate speed clutch I2, a gear H0 freely rotatableon the shaft section I6 and held against axial movement between a peripheral flange IIS on the latter and the disk II. a gear I20 freely rotatable in fixed axial position between the keys 63 and a peripheral flange I2I on the shaft section 40, and a clutch I22 to the intermediate shaft section 41.- diate speed drive, the gear ratio is higher, and the torque to which the clutches I I and I2 are subjected is lower for a given load than in th previously described high. speed drive.

The clutch I2 may be of any suitable overload type. Since it serves the same function in the intermediate speed drive as does the clutch II in the high speed drive, both clutches preferably are alike in construction. comprises two annular end face elements I23 and I24 which are formed respectively on the sleeve member 31 and on one side of the gear H8, and which have opposed ratchet teeth. The

gear H8 is formed with an annular groove I25 adapted to receive the free end of the sleeve 36 when the clutch I2 is closed. The axial position of the clutch element I23 is automatically controlled by the keys 35 and 36 which are inclined or helical to convert the torque partially into an axial thrust component tending to open the clutch I2, and by a plurality of U-shaped compression springs I26, anchored at their free ends to pins I21 and.l20 respectively on a disk I29 rigid with the element I23 and an opposed disk I30 integral with the shaft section I5, and tending to rotate the sleeve 31 on the shaft section I5 to advance the clutch element I23 by a screw action into engagement with the element I24. The disk I29 has a plurality of lateral projections I3I, one for each set of springs I26, and the disk I30 has an annular side flange I32 overlying the projections.

The clutches II and I2 operate in the same way. However, due to the increased gear ratio in the intermediate speed drive, the load on the driven shaft assembly I0 at which the clutch l2 will open is greater than that necessary to open the clutch I I. The sequencein which the clutches II and I2 operate may also be varied by selec- In the interme-' sleeve 65, and which are. formed respectively closed, the clutch I2 will also be closed. To prevent both clutches II and I2 from being connected simultaneously to the driven shaft assembly I0, the second clutch I22 is interposed in the intermediate speed drive. The clutch I22 in its preferred form comprises .two annular end face elements I33 and I34 which are rigid respectively with the adjacent sides of the gear I20 and the with coacting ratchet teeth. It will be evident that the clutch element I34 is constantly con-, nected to the intermediate shaft section 41, and is movable axially into and out of engagement with the element I33. v to close the clutch I22. In the present instance, this means comprises a ring I35 encircling the sleeve 65 and having a plurality of parallel annularly arranged plungers I35 slidable in the disk Springs I36 disposed about the plungers I35 and confined between the disk and the ring I35 press the latter against the member 65. However, the spline keys- 63 and 64 control the position of the clutch element I34 automatically in response to the reaction of the shaft section 41. clined or hell Gal relative to the axis of rotation, the direction of inclination being such that power rotation of the shaft section 48 against the resistanceof the section 41 will impart an axial thrust on the clutch element I33 to open the clutch I22. When the drive to the section 48 is disconnected, the springs I36 will close the clutch I22.

The low speed drive, which is adapted to carry the maximum load, as for example in starting a motor vehicle, is taken from a gear I31 rigid with the shaft section I6, through a gear I38 meshing with the gear I31 and freely rotatable in fixed axial position on the intermediate shaft section 41 between the disk 10 and the keys 13,.

and the low speed clutch I3, to the intermediate shaft section 46. 1

The clutch I3 preferably is the same in construction as the clutch I22. Thus, the clutch I3 comprises opposed annular clutch elements I39 and I40 which are rigid respectively with the gear I38and the sleeve 15, and which are formed with coacting ratchet teeth. A ring I having plungers I4I slidably mounted in the disk 80 is pressed by springs I42 against the clutch ele-v ment I40, and tend to urge the latter into engagement with the element I39. The spline keys l3 and I4 are inclined or helical, so that when the shaft section 41 is disconnected from the inlet shaft assembly 9, the clutch I3 will close automatically under the action of the springs I42,- and when the section 41 is driven it will overrun the sleeve to open the clutch I3. I Means may be provided, if desired, for automatically utilizing the braking action of the motor when the power therefrom is discontinued. Such means is shown in the present instance, and comprises a gear I43 fixed on the shaft section I6 andmeshing with a gear I44 freely rotatable in fixed endwise position on the intermediate shaft section 45 between the clutch 93 and the keys 83; An automatic clutch I45 is adaptedto connect the gear I44 to the outlet shaft sec- Yieldable means tends Thus, the keys 63 and 64 are slightlyv in-' face clutch elements I46 and I41 which are integral respectively with the gear I44 and the sleeve 85, and which are formed respectively with coacting ratchet teeth orientated to effect a drive in a counterclockwise direction as viewed in Fig. 6. A ring I48 having plungers I48 slidable in the disk 90 is urged by springs I49 against the clutch element I41, and tend to move the latter into engagement with the element I46. The keys 83 and 84 are helical or inclined in a direction such that, when the power drive to the shaft section 45 is discontinued, the rotation of the outlet shaft section 44 through the momentum of the driven part, as for example the motor vehicle, will cause the clutch I45 to close, and when the power drive is operative, the shaft section 45 will overrun the shaft section 44 to open the clutch I45. If the driven part is idle, the springs I49 will close the clutch I45. 'As a result, when the power drive is discontinued, the source of power, as forexample the engine, re-

sists' rotation of the outlet shaft section 44 to is joumalod at one end in the wall 22. The

other end of the shaft I52 has a reduced axial extension I53, and is keyed to the inside element I54 of an overrunning clutch I55. A short shaft I56 journaled in the end wall I8 has an axial bore I51 receiving the projection I53, and carries the outside element I58 of the clutch I55. Disposed in notches I59 in the periphery of the clu'ch element I54 are wedge rollers I60 adapted to lock the clutch I55 upon rotation of the shaft I52 in a counterclockwise direction. A gear I6I rigid with the element I58 is connected through a gear I62 rotatable on the shaft section 48 to a gear I63 rigid with the clutch element IOI. Preferably, all of the clutches 98, 93 and I55 are alike in construction.

The gear I01 bears a ratio to the gear I06 the same as that of the gear I50 to the gear I5I. All of the gears I6I, I62 and I63 are the same in size. Hence, the elements I00 and II are rotated at the same speed when the transmission is driven from the shaft section 44.

The operation of the transmission will be evident from the foregoing, and briefly described is as follows:

With the driving and driven shaft assemblies 9 and I0 stationary, all of the clutches are closed. When power is applied to'the shaft 99, the overrunning clutch 98 operates to drive the shaft assembly 9 in a clockwise direction. Initially,

the high speed drive through the clutch II takes up the small amount of slack or lost motion in the clutches, and then causes the clutches I2, I 3, I22 and I to open. It will be understood that the overrunning clutch 93 maintains the drive connection to the outlet shaft section 44 in a counterclockwise direction. However, after the slack has been taken up, the resistance to movement of the driven part acts through the driven shaft assembly I0 to exert a heavy torque which causes the high speed clutch II to open. The clutches I2 and I22 tend to 'close through the action of the springs I26 and I36, but fail to establish the intermediate speed drive-since the torque is still too great. The low speed clutch I3, however,

closes in response to the action of the springs I42, and hence the low speed drive is connected. It will be understood that the clutch I45 remains open at all times during the drive of the shaft section 44 from the driving shaft assembly 9.

As'the speed of the driven part is increased, less power is required, and hence the driving torque is gradually decreased until the clutches sion automatically selects the proper gear ratio for a given load. In accelerating from one speed to another, the momentum is increased to a point such that the torque'necessary to drive the shaft 44 is reduced sufiiciently to compensate for the change in gear ratio.

It will be understood that the driving torque is determined by the degree of power applied to the inlet shaft 99. When the momentum of the car is increas d; less power is required. In any speed, a sud en or sharp acceleration may increase the torque to a point that the drive will shift. I

When the power is discontinued to stop the drive, the momentum of thedriven part causes the shaft section 44 to continue rotating in a counterclockwise direction. As a result, the braking clutch I45 closes to drive the shaft section IS. The sections I6 and I5 respectively overrun the sections I 5 and I4 to lock the clutches I I and I2 in closed position so that the driving shaft assembly 9 rotates as a unit. From the shaft assembly 9, the drive is transmitted to the shaft section 48. Hence, the clutches I3 and I22 are open. The drive continues from the shaft assembly III through the backshaft I52, the clutch I55 and the gears I 6|, I62 and I63 to the shaft 99, thereby utilizing the motor or source of power to brake the movement of the driven part.

While I have shown clutches of the positive type, it will be understood that friction clutches may be used. Also, by eliminating or interrupting the back drive through the shaft I 52, free wheeling characteristics can be obtained.

I claim as my invention:

1. An automatic adjustable-speed gear transmission comprising, in combination, two axially aligned drive shaft sections coupled together for joint rotation, two axially aligned driven shaft sections coupled together for joint rotation, a relatively low speed gear connection between one of said drive sections and one of said driven sections and including an automatic. clutch adapted to open in response to a drive from the other driven section, and a relatively higher speed gear connection between the other of said drive sections and said other driven section and including aligned drive shaft sections coupled together for Joint rotation, two axially aligned driven shaft sections coupled together for joint rotation, a relatively low speed gear connection between one of said drive sections-and one of said driven sections, an automatic clutch in said connection and adapted to close in response to a spring pressure and having an actuator operable by the other driven section to open said clutch against the spring pressure in response to a drive from the other driven section, and a higher speed gear connection between the other of said drive sections and said other driven section and including an automatic overload release clutch and an automatic clutch in series, said overload clutch being adapted to open in response to a torque in excess of a predetermined value and to close in responseto a torque below said value, said'last mentioned automatic clutch being adapted to close in response to spring pressure.

3. An automatic adjustable-speed gear transmission comprising, in combination, three axially aligned drive shaft sections coupled together for joint rotation, three axially aligned driven shaft sections connected together for joint rotation by couplings permitting a limited lost motion between each set of adjacent sections, a low speed gear connection adapted to connect one drive section to one driven section and including a normally closed automatic clutch which will operi in response to the intermediate driven section overrunning said one driven section, an intermediate speed gear connection for connecting the intermediate drive section to said intermediate driven section and including an automatic overload clutch responsive to the torque of said drive sections, and including a normally closed automatic clutch which will open in response to said other driven section overrunning said intermediate driven section, and a high speed gear connection for connecting the other drive section to said other driven section and including an comprising, in combination, three axially aligned drive shaft sections coupled together for joint rotation, three axially aligned driven shaft sections, a plurality of lost motion couplings connecting said driven sections for joint rotation, a low speed connection adapted to connect one drive section to one driven section and including an automatic clutch adapted to open when the intermediate driven section overruns said one driven section through the lost motion in the connection coupling, an intermediate speed connection for connecting the intermediate drive section to said intermediate driven section and including an automatic overload clutch responsive to the torque of said drive sections, and including an automatic clutch adapted to open when said other driven section through the lost motion in the connecting coupling overruns said intermediate driven section, and a high speed connection for connecting the other drive section to said other driven section and including an automatic overload clutch' responsive to the torque of said drive sections.

5. An automatic adjustable-speed gear transmission comprising, in combination, a power inlet and a power outlet, each having a plurality of axially aligned shaft sections connected for joint rotation, a plurality of parallel gear connections of different gear ratios for connecting the respective shaft sections of said inlet to the respective shaft sections of said outlet, the'connection oi the lowest gear ratio including an automatic clutch adapted to open in response to a driVe from the other connections, the connection of the next lowest g ear ratio including an automatic overload clutch adapted to open in response to a torque in excess of a predetermined value and to close in response to a torque below said-value.

6. An automatic adjustable-speed transmission comprising, in combination, a power inlet and a power outlet, each having a plurality of axially aligned shaft sections connected for joint rotation, a plurality of parallel connections of different speed ratios for connecting the respective shaft sections of said inlet to the respective shaft sections of said outlet, one connection of a relatively low speed ratio including an automatic clutch adapted to open in response to a drive from a connection of a higher speed ratio, said last mentioned connection including an automatic overload clutch adapted to open in response to a torque in excess of a predetermined value and to close in response to a torque below said value.

'7. An automatic adjustable-speed transmission comprising, in combination, a power inlet, a power outlet, and a plurality of parallel drive connections of different speed ratios selectively available to connect said inlet to said outlet, said connections respectively including automatic clutches adapted to be closed by spring pressure and having actuators operable from said power inlet to permit closing of said clutches in a predetermined sequence in response to a, progressive decrease in torque on the power inlet to close said connections successively in the order of increasing speed ratios.

8. An automatic adjustable speed transmission comprising, in combination, a drive shaft assembly having a plurality of interconnected shaft sections, a driven shaft assembly having a plurality of interconnected shaft sections, and a plurality of drive connections from the respective drive shaft sections to the respective driven shaft sections, said connections respectively including a plurality of automatic clutches adapted to be closed by spring pressure and having actuators operable from said drive shaft to permit closing of said clutches in a predetermined sequence upon a progressive decrease in torque on said drive shaft to complete said connections successively. 4

9. An automatic adjustable speed transmission comprising, in combination, a power inlet, a power outlet, and a plurality of parallel drive connections of different speed ratios selectively available to connect said inlet to said outlet, said connections respectively including automatic clutches adapted to be closed by spring pressure and having actuators operable from said power inlet to permit closing of said clutches in a predetermined sequence in response to a progressive decrease in torque on the power inlet to close said connections successively in the order of increasing speed ratios, each connection upon closing effecting the opening of any other connection of a lower speed ratio.

10. An automatic adjustable speed transmission comprising, in combination, a drive shaft assembly having a plurality of interconnected shaft sections, a driven shaft assembly having a plurality of interconnected shaft sections, a plurality of drive connections from the respective drive shaft sections to the respective driven shaft sections, said connections respectively including a plurality of automatic clutches adapted to be closed by spring pressure and having actuators operable from said drive shaft to permit closing of said clutches in a predetermined sequence upon a progressive decrease in torque on said drive shaft to complete said connections successively, and a connection for driving said drive shaft assembly from said driven shaft assembly and including an automatic reverse clutch operable to close when said driven shaft assembly overruns said drive shaft assembly, and to open when said drive shaft assembly overruns said driven shaft assembly.

11'. In a transmission, in combination, two

axially aligned shaft sections, a coupling member keyed to one of said sections, a second coupling member having a helical spline connection with the'other'of said sections permitting axial movement of said second member, a spline connection between said members permitting relative axial movement therebetween, a gear freely rotatable on said other section, and two opposed annular end face clutch elements with coacting teeth rigid respectively with said secondcoupling member and said gear and constituting an automatic clutch adapted through the action of said helical spline connection to open when said other section overruns said one section and to close when said one section overruns said other section.

12. In a transmission, in combination, two axially aligned shaft sections, a coupling member rotatable with one of said sections, a second coupling member having a spline connection with the other of said sections permitting a limited rotary axial movement of said second member over said other section, a spline connection between said members permitting relative axial movement therebetween, and two opposed clutch elements, one of said elements being rigid with said second coupling element member for movement into and out of coacting engagement with the other of said elements, said elementscon stituting an automatic clutch adapted through the action of. said first mentioned spline connection to open when said other section overruns said one section and to close when said one section overruns said other section.

13. In a transmission, in combination, .two axially aligned rotary shaft sections, a first coupling member fixed for rotation with one of said sections, a second coupling member splined for axial movement on the other of saidsections and connected to said first coupling member for rotation therewith, and a clutch for driving said second member, said clutch including a driving element, and a driven element rigid with said second coupling element for rotation therewith.

14. In a power transmission, a shaft assembly comprising a plurality of axially aligned end and intermediate sections splined together for joint rotation, one end section having an axial bore, the other end section having a reduced axial extension projecting into said bore, and each intermediate section being tubular in form and disposed on said extension between said end sections, all of said sections being in end abutment.

15. In a power transmission, a shaft assembly comprising a plurality of separable axially aligned shaft sections mounted in interfitting and selfaligning relation, and means coupling said sections for joint rotation, and permitting a limited relative rotation between said sections.

16. In a power transmission, a shaft assembly comprising a plurality of separable axially aligned shaft sections one section having an axial bore in, one end, another section rotatably extending providing a limited angular lost motion therebetween.

1'7. In a power transmission, a shaft assembly comprising a plurality of axially aligned end and intermediate sections, one end section having an axial bore, the other end section having a reduced axial extension rotatably projecting into said bore, and each intermediate section being tubular in form and rotatably disposed on said extension between said end sections, and a plurality of couplings respectively connecting the adjacent sections for joint rotation, and permitting relative rotation therebetween through a limited lost motion.

18. In a-power transmission, a shaft assembly comprising a plurality of axially aligned end and intermediate sections, one end section having an axial bore, the other end section having a reduced axial extension rotatably projecting into said bore,

and each intermediate section being tubular in form and rotatably disposed on said extension between said end sections, all of said sections being in end abutment, and a plurality of couplings connecting said sections of joint rotation, each coupling comprising two members encircling adjacent sections and having an axially slidable key connection with each other, and axially slidable key connections respectively with said adjacent sections, said sections and said coupling members being held in assembled relation by said end sections and being subject to disassembly by relative axial stripping movement.

19. In a power transmission, a shaft assembly comprising a plurality of axially aligned end and intermediate shaft sections, and a plurality of couplings connecting said sections for joint rotation, each coupling comprising two members encircling adjacent sections and having an axially slidable key connection with each other and axially slidable key connections respectively with saidadjacent sections, said sections and said coupling members being held'in assembled relation by said end sections and being subject to disassembiy by relative axial stripping movement.

20. A clutch comprising, in combination, an axially fixed driven clutch element having an annular end face with serrated clutch teeth, a drive shaft, a driving clutch element having an annular end face with serrated clutch teeth adapted to coact with said first mentioned teeth. and having a spline connection with said shaft permitting axial movement of said driving element into and out of engagement with said driven element, said spline connection being helical to resolve the torque of said driving element into an axial component of thrust tending to urge said elements apart, and spring means tending to urge said driving element into engagement with said driven element.

21. A clutch comprising, in combination, a driven clutch element having an annular end face, a drive shaft, a driving clutch element having an annular end face adapted to coact with said first mentioned face and having'a spline connection with said shaft permitting axial movement of said driving element into and out of engagement with said driven element, said spline connection having a face inclined to the axis of :rotation and adapted to resolve the torque of said driving element into an axial component of. thrust tending to urge said elements apart, and spring means tending to urge said driving element axially into engagement with said driven element.

JOHN MISIAK, J R.

CERTIFICATE OF CORRECTION.

Patent No. 2,042,235. I May 26, 1956,

JOHN MISIAK, JR;

It is hereby certified that error appears in the printed specification of the above numbered patent requiring correction as follows; Page 5, second column, line 53-54, claim 4, for the word "connection" read connecting; and lines 60-61 claim 4, strike out the words "through the lost motion in the connecting coupling" and insert the same after "section" and before the comma in line 62, same claim; page 6, second column, line 58, claim 12, strike out the word "element"; and that the said Letters Patent should be read with these corrections therein that the same may conform to the record of the case in the Patent Office.

Signed and sealed this 25th day of August, A. D. 1956.

, Leslie Frazer (Seal) Acting Commissioner of Patents. 

